US3826437A - Demolition mill - Google Patents

Abstract

A demolition mill for solid debris utilizes free swinging demolition hammers rotatably mounted on shafts interconnecting solid metal wheels journaled in a housing. The hammers extend radially of the wheels under the action of centrifugal force to break, shatter or pulverize all kinds of solid debris. A hydraulic feed rotor is journalled adjacent the housing inlet and includes a cylindrical feed roller driven by a hydraulic motor mounted in a tube positioned within the roller. Lengths of chain or serrated bars welded to the periphery of the roller assist in feeding material to the hammers.

Description

United States Patent [191 1111 3,826,437 Warren, Jr. et al. 1 July 30, 1974 DEMOLITION MILL Primary ExaminerRoy Lake [75] Inventors: Fred E. Warren, .lr., Tigard; Asst-am Examiner-E F.Desmond Kenneth F. Fling, Sherwood; Gary Attorney, Agent, or Fzrm-Klarqutst, Sparkman,

R. Moore, Hillsboro, all of Oreg. Campbell Leigh & Whinston [73] Assignee: Ecolo-Tech, Inc., Sherwood, Oreg.

22 Pl d F b l [57] ABSTRACT 1 l e e 1973 A demolition mill for solid debris utilizes free swinging PP 333,401 demolition hammers rotatably mounted on shafts interconnecting solid metal wheels journaled in a hous- 152 11s. c1 241/186 R, 241/101.7, 241/195 hammersfaxtend radially the wheels under [51 1m. (:1. B02 13/04 the cemnfuga force break Shatter [581 Field of Search 241/185 R 186 R 101 M verize all kinds of solid debris. A hydraulic feed rotor 241/101 7 i is journalled adjacent the housing inlet and includes a cylindrical feed roller driven by a hydraulic motor [56] References Cited Lengths of chain or serrated bars welded to the pe- UNITED STATES PATENTS riphery of the roller assist in feeding material to the 1,266,894 5/1918 Williams 241/195 hammers, 3,482,788 12/1969 Newcll 24l/l94 X 5 Claims, 8 Drawing Figures mounted in a tube positioned within the roller.

1 DEMOLITION MILL BACKGROUND OF THE DISCLOSURE This invention relates to demolition and disposal machines for breaking, shattering and pulverizing solid waste debris.

With environmental clean-up rules becoming increasingly restrictive, a versatile and tough, all-purpose demolition and disposal machine for breaking, shattering or pulverizing solid waste material has become a necessity.

Such a machine to be successful must be capable of handling all types of material, such as bark, green wood, seasoned timber with nails, and the products of building demolition including such diverse items as conduit, junction boxes, metal gutters, roofing and such problem materials as glass, brick and plasterboard. Additionally, such, a machine must be capable of disposing of brush, root mass with sod and stones, as well as the byproducts and debris from logging operations.

Reduction in size of waste materials such as the above leads to their most efficient disposal since such material can then be recycled or used as ground cover, fill or for erosion control. If waste material is pulverized fine enough, it can be distributed by conventional roadside spreading methods.

Accordingly, it is the primary object of the present invention to provide a demolition and disposal machine for breaking, shattering or pulverizing all types of solid waste and debris.

It is a further object of the present invention to provide such an apparatus that will be tough and rugged and which can quickly reduce the size of material of the type heretofore described without damage to itself.

It is a still further object of the present invention to provide such an apparatus that can produce an end product of a size to suit the desires or needs of the operator.

It is a still further object of the present invention to provide such an apparatus that can operate at a rate commensurate with a crew s ability to feed it.

SUMMARY OF THE INVENTION The disposal machine of the present invention comprises a housing defining an inlet throat and an outlet, and a demolition rotor journaled in the housing on a generally horizontal axis extending in a direction transversely of the throat.

The demolition rotor comprises at least two wheels mounted for rotation about the axis and a plurality of circumferentially uniformly spaced shafts interconnecting the wheels adjacent the peripheries thereof, the shafts being adapted to revolve with the wheels about the axis.

A plurality of free swinging demolition hammers are rotatably mounted on each of the shafts. The hammers extend radially of the wheels under the action of centrifugal force when the wheels rotate about the rotor axis for striking contact with material fed into the housing inlet. The hammers hang vertically from the shafts when the rotor is at rest.

Means are provided operatively to connect the rotor with a source of power for rotating the rotor at a speed sufficient to cause the hammers to demolish the material fed into the housing.

The hammers are mounted on the shafts in a manner such that the hammers on one shaft interleave with those mounted on an adjacent shaft when the wheels are at rest, thereby to avoid interference with each other. The spacing of the hammers, however, is such as completely to cover the entire lateral distance between the wheels, thus insuring contact with every bit of material fed into the rotor.

The hammers themselves are free swinging, 360 rotatable plates having their longitudinal axes disposed radially of the wheels when the latter are rotating. A hammer plate is attached to a shaft by means of an aperture positioned at one end of the plate, the other end of the plate being symmetrically curved concavely inwardly. The sides of each plate are also symmetrically curved concavely inwardly, so that each of the sides forms an acute angle cutting corner with the end of the plate. When such cutting corners become worn after extended use, reversal of the entire rotor assembly places the opposite cutting corners in striking position. Subsequent erosion of the ends of the plates results in a regeneration of the initial end curvature, thereby to achieve a self-sharpening of the hammers.

A feed rotor journalled adjacent the inlet throat provides braking and regulated control over material fed to the demolition rotor. The feed rotor comprises a generally symmetrical feed roller, and motor receiving means disposed within the roller and connected to the apparatus frame. Hydraulic motor means mounted in the receiving means drivingly connects to the feed roller, which rotates on bearing means mounted on the motor receiving means. Means attached to the outer peripheral surface of the feed roller assist in feeding material to be demolished into the inlet throat.

BRIEF DESCRIPTION OF THE DRAWINGS on line 55 of FIG. I and illustrating the construction of the feed rotor of the present invention.

FIG. 6 is a sectional view taken on line 6-6 of FIG. 5.

FIG. 7 is a side view of a portion of a feed roller illustrating an alternate embodiment of feeding means attached to the outer peripheral surface thereof.

FIG. 8 is a sectional view taken on line 8-8 of FIG. 7.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to the drawings, the demolition mill 10 of the present invention includes a heavy duty 2-wheel trailer frame 11 having high flotation tires 12 on adjustable side mounted stub axles 13. A front draw bar 14 is provided for towing. A diesel engine 15 providing or more B.H.P. and mounted on the frame 1] drives a demolition rotor 16 journalled in a housing 17 through 3 a power takeoff 18 and a belt drive 20. The engine also furnishes power through an auxiliary belt drive 21 to a hydraulic pump (not shown) located in a gallon hydraulic reservoir 22 mounted behind the engine 15 on the frame 11.

Hydraulic lines 23 with appropriate directional control valves carry hydraulic fluid under pressure from the reservoir 22 to a hydraulic motor 24 for a feed rotor 25 positioned rearwardly of the demolition rotor 16 and to another hydraulic motor 26 which drives a belt conveyor 27 positioned on the bottom 28 of a rearwardly disposed foldable feed hopper 30. Broken, shattered and pulverized debris from an outlet 31 in the housing 17 is carried through an exhaust chute 32 mounted on supports 33 forwardly of the apparatus to a point of disposal.

A feature of the invention resides in the demolition rotor 16 which is illustrated in greater detail in FIGS. 3 and 4. Three one-half inch thick solid circular steel 20 inch diameter end plates or wheels 34 having hubs 34a and mounted 9 inches apart are keyed for rotation with a horizontal center shaft 35 journalled in bearings 36 on opposite sides of the housing 17. Each wheel 34 has, in the apparatus shown, nine drilled and induction hardened holes 37 circumferentially uniformly spaced adjacent the periphery 38 thereof. A 1.25 inch diameter steel cutter shaft 39 preferably made of 4,140 steel fully hardened to Rc'50/55 is received in a machinefit in each set of opposed holes 37 to interconnect adjacent wheels 34. Shafts 39 thus revolve with the rotor 16. about its horizontal axis 40.

The housing 17 is preferably made of 5/8 inch thick Tl (armor) plate to provide suitable protection against the hazards of breaking hammers and demolished material. Horizontal plates 42 and 43 welded to the cylindrical portion 44 of housing 17 providean inlet 45 having a cross section 12 by l8 inches in size and which is positioned such that its upper surface 46 is coplanar with the horizontal radial plane 47 through the axis 40, the lower surface 48 of the inlet 46 being slightly above the lower horizontal tangent to the cylindrical portion 44. The outlet 31 is formed by an upper plate 50 and a lower plate 51 welded to the opposite or downstream side of the portion 44 at a location generally opposed to that of the inlet 45, and 'the entire housing assembly is bolted to the frame 11 through elongated slots (not shown) to provide longitudinal adjustability as required.

A plurality of free swinging, 360 rotatable demolition hammers 52 are rotatably mounted on each of the nine shafts 39 such that the hammers can extend radially of the wheels 34 under the action of centrifugal force when the wheels rotate. In the embodiment illustrated, six such hammers 52 are positioned on each shaft 39 between adjacent wheels 34, i.e., a total of 12 hammers on each of the nine shafts 39. Spacers 53 are provided in between each hammer and the hammers are spaced on the shafts 39 ina manner such that the hammers mounted on one shaft interleave with the hammers mounted on an adjacent shaft when the rotor is stationary and the hangers are hanging vertically from the shafts, thereby to avoid interference with each other. The spacing of the hammers on the shafts, however, is such as completely to cover the entire distance between adjacent wheels 34 so that at least one hammer will contact each piece of material irrespective of its lateral position with respect to the wheels 34 as long as the material is within striking range of the hammers.

A preferred hammer spacing pattern is illustrated in FIG. 4, wherein the wheels 34 have a diameter of 20 inches and are positioned 9 inches apart. For convenience the nine shafts 39 are identified by numerals 39a-39i, inclusively; the three wheels by numerals 34a-34c, inclusively.

In the example shown the first shaft 39a rotatably supports six such hammers 52 between the wheels 34, the innermost ones being immediately adjacent the center wheel 34b. On the next adjacent shaft 39b the hammers are positioned such that there is equal spacing as between the outermost hammers and the adjacent wheels. On the next shaft 39c the hammers are spaced such that the outermost ones are adjacent the outer wheels 34a and 340.

The hammers are mounted on shaft 39d such that the innermost ones occupy an intermediate position as respects those on shaft 39b. The hammers are mounted on shaft 39e in a manner which is a mirror image of those on shaft 39d. The hammers are mounted on shaft 39f with slightly less space between the position of the innermost hammer than is present in shaft 39d. The position of the hammers on shaft 393 is such as to provide slightly more space inboard of the innermost hammer than is present on shaft 39b. The position of the hammers on shaft 39h is the same as on shaft 39a and the position of the hammers on shaft 39i is the same as it is on shaft 39b.

Other spacing patterns are, of course, possible, the only requirements being the necessity to avoid interference when the rotor 16 is at rest and the further necessity to .cover the entire distance between the wheels 34 to insure striking contact throughout the entire zone.

Each of the hammers 52 comprises a cutting tooth 54 formed from a generally rectangular fully hardened piece of 4,]40 or 4,340 steel plate preferably 6 inches by 2% inches by 0.375 inch thick. The teeth are preferably fully hardened in a salt bath to Re 50/55. Each tooth is provided with an aperture 55 adjacent one end 56 for receiving one of the shafts 39, the aperture 55 being located on the longitudinal center line or axis 57 of the tooth. As will be understood, the center line 57 is disposed radially of the wheels 34 when the latter rotate.

The opposite end 58 of each tooth is cut in the form of a symmetrical inwardly-concave curve at a preferred radius of 3.25 inches. The sides 60 of the tooth are similarly symmetrically and inwardly-concavely curved on identical 3.25 inch radii. The sides 60 and the end 58 of a tooth thus form on each side a relatively sharp cutting corner 61 having the acute angle shown.

We have found that the clearance between the housing 17 and the hammers 52 is not critical inasmuch as the hammers do not operate by cutting the material, but rather operate on a ballistic principle, the teeth 54 just shattering the material as they come in contact therewith. Also, since the hammers 52 are freely rotatable on the shafts 39, the support for the rotor 16 can be less rigid than otherwise, making it possible to journal the rotor in the housing 17 as we have described.

Operation of the rotor 16 unavoidably causes wear on the striking corners 61 of the teeth 54, which wear ultimately causes them to become round. We have discovered, however, that if the entire rotor 16 be reversed in the housing 17 such that operation of the apparatus brings the opposite cutting corners of the hammers into striking position, the wiping effect of material, as it passes along the ends 58 of the teeth as the material is being demolished, causes a totally unexpected sharpening of the previously dulled or rounded opposite striking corners. This wiping effect causes a regeneration of the original end curvature as the teeth wear down in length, thereby resulting in an effective resharpening of the acute angle cutting corners on the opposite and theretofore dull sides. We have found that the pulverizing of concrete is particularly effective in resharpening of the teeth due to the erosion caused by the wiping action of the material on the ends 58. We have been able to operate for as long as 3,000 hours on a given set of teeth.

With 108 hammers working in the rotor (12 hammers on each of nine shafts), normal operation provides 237,000 striking contacts per minute with in excess of 2,000 pounds of force per strike. This has been demonstrated to be sufficient to break up 5 inch wide by 5/8 inch thick mild steel plate with no appreciable damage to the hammers.

When demolishing building debris, the rotor can handle up to and including inch water pipe, junction boxes, metal gutters and similar items. Glass, brick, plasterboard and even rock can be pulverized. Other items that can be handled by the rotor are seasoned timbers with spikes, conduit, door knobs, roofing debris and drain gutters, green and round wood, brush as well as root mass with sod and stones, slab bark including both redwood and cedar bark, paper and cardboard scrap, tin cans, bottles, wet garbage, composition materials, and insulating remnants. The force of the rotation eliminates the necessity of a blower, although such could be incorporated if desired, the pulverized debris being discharged merely by the operation of the rotor 16 through the exhaust chute 32.

A further feature of the invention resides in the feeding apparatus. The foldable hopper 30 has a bottom 28 and outwardly flaring sides 64 and is disposed rear wardly of the rotor 16 and housing 17. The hopper 30 is provided with a belt conveyor 27 supported on end rollers 65 and driven by the hydraulic motor 26 which is powered by hydraulic fluid under pressure from the reservoir 22 and operated by suitable controls 66. The foldable nature of the hopper facilitates transportation of the apparatus.

A pair of generally L-shaped arms 67 are pivotally attached to the housing 17 on each side thereof immediately adjacent wear plates 68 positioned at the top, each of the arms 67 being vertically movable by means of a hydraulic cylinder 70 and piston 71 mounted on the frame 11 and pivotally attached to the arm 67 by a clevis 72. The feed rotor 25 is supported by the arms 67 adjacent the inlet 45 for rotation on an axis 73 parallel to the axis 40 of the demolition rotor 16, such that extension of the pistons 71 causes the arms 67 to lift the rotor 25 should such be desired.

As shown in FIGS. 5 and 6, the rotor 25 includes a I cylindrical feed roller 75 having an end plate 76 fitted with a stub shaft 77 for rotation in a bearing 78 mounted on one of the arms 67a. The roller 75 is provided with an intermediate web 80 having a centrally located hub 81 welded thereto and an additional annular web 82 welded adjacent its opposite end 83 for a purpose hereinafter to be described.

The hydraulic motor 24 serviced by the hydraulic lines 23 from the reservoir 22 is positioned in a motor tube 84 which is positioned interiorly of the roller 75, the tube 84 having an access opening 85 at the top thereof, the motor 24 being attached to an end wall 86 of the tube 84 by bolts 87 and having a drive shaft 88 connected to the hub 81 by a key 90. A bearing flange 91 welded to the outer end 92 of the motor tube 84 has a cylindrical extension 93 threaded at its end 93a and which extends outwardly of the roller 75 through the annular web 82.,The extension 93 has a central bore 93b to accommodate the lines 23 and supports a bearing 94, the outer race 95 of which is keyed to a bearing ring 96 attached to the web 82 by bolts 97. A locking collar 98 is received on the extension 93 being retained by a set screw 100, the extension 93 being locked to the arm 67b by a key 101 and the entire assembly being retained by spanner nuts 102 and a lock washer 103 as shown. Hydraulic power to the motor 24 causes rotation of the drive shaft 88 and consequent rotation of the feed roller 75 in the bearing 78 and about the inner race 104 of the bearing 94 at the other end 83, the assembly providing for efficient placement of the hydraulic motor 24 yet ready access thereto by means of the opening 85 in the tube 84. I

In operation the feed rotor 25 actually functions as a brake, floating on the debris fed into the hopper 30 by pivotal action of the arms 67. The feed rotor 25 and the conveyor 27 are operated in series to regulate control over the rate at which material is fed into the demolition rotor 16, thereby to permit the production of various sized end products to suit the desires or needs of the operator. Adjusting the speed of the conveyor 27 and the rotational speed of the roller 75 also permits the apparatus to operate at a rate suited to the crews ability to feed material to it.

Means in the form of chains 106 welded to the outer peripheral surface 107 of the feed roller 75 at circumferentially spaced intervals therearound assist in the feeding of material into the inlet throat 45. The chains 106 are a desirable feeding means for garbage and general refuse.

As shown in FIGS. 7 and 8, alternatively the feeding means can take the form of serrated bars 108 welded to the outer peripheral surface 107a of a roller 75a at circumferentially spaced intervals therearound, the bars 108 having their ends 109 bent at an angle to the elements 110 of the cylindrical surface 107a as shown. The serrated or toothed construction is desirable for disposal of material such as railroad ties and wood having loose bark.

Utilizing hydraulic power for the feed roller 75 and the conveyor 27 makes it possible to extend the use of the apparatus to a variety of auxiliary tools such as hydraulic saws which can be coupled to the hydraulic system as desired. The hydraulic system also makes it possible to incorporate an emergency safety stop system.

We claim:

1. In a demolition mill having frame means, housing means mounted on said frame means and defining an inlet throat and an outlet, a demolition rotor journalled in said housing means on a first generally horizontal axis extending in a direction transversely of said throat, a plurality of hammer elements carried by said rotor for demolishing material fed into said inlet throat, means for imparting rotation to said demolition rotor and a source of hydraulic fluid under pressure,

a feed rotor journalled adjacent said inlet throat on an axis parallel to said first axis, said feed rotor comprising a generally cylindrical feed roller, motor receiving means disposed within said feed roller and connected to said frame means,

hydraulic motor means mounted in said motor receiving means and drivingly connected to said feed roller,

means connecting said hydraulic motor means to said source of hydraulic fluid,

bearing means mounted on said motor receiving means, said feed roller being adapted to rotate on said bearing means, and means attached to the outer peripheral surface of said feed roller for feeding material into said inlet throat.

2. The feed rotor of claim 1 further comprising a pair of arm means pivotally connected to said housing means and extending on opposite sides of said feed roller,

said motor receiving means being attached at one end to one of said pair of arm means,

said bearing means being mounted on said motor receiving means at said one end thereof, said feed roller rotation on said bearing means at one end of said feed roller,

said feed roller being journalled at its other end in the other of said pair of arm means.

3. The feed roller of claim 2 further comprising web means disposed within said feed roller, said hydraulic motor means being drivingly attached to said web means adjacent the other end of said motor receiving means.

4. The feed rotor of claim 1 in which said feeding means comprise chain means.

5. The feed rotor of claim 1 in which said feeding means comprise serrated means.

Claims (5)

1. In a demolition mill having frame means, housing means mounted on said frame means and defining an inlet throat and an outlet, a demolition rotor journalled in said housing means on a first generally horizontal axis extending in a direction transversely of said throat, a plurality of hammer elements carried by said rotor for demolishing material fed into said inlet throat, means for imparting rotation to said demolition rotor and a source of hydraulic fluid under pressure, a feed rotor journalled adjacent said inlet throat on an axis parallel to said first axis, said feed rotor comprising a generally cylindrical feed roller, motor receiving means disposed within said feed roller and connected to said frame means, hydraulic motor means mounted in said motor receiving means and drivingly connected to said feed roller, means connecting said hydraulic motor means to said source of hydraulic fluid, bearing means mounted on said motor receiving means, said feed roller being adapted to rotate on said bearing means, and means attached to the outer peripheral surface of said feed roller for feeding material into said inlet throat.

2. The feed rotor of claim 1 further comprising a pair of arm means pivotally connected to said housing means and extending on opposite sides of said feed roller, said motor receiving means being attached at one end to one of said pair of arm means, said bearing means being mounted on said motor receiving means at said one end thereof, said feed roller rotation on said bearing means at one end of said feed roller, said feed roller being journalled at its other end in the other of said pair of arm means.

3. The feed roller of claim 2 further comprising web means disposed within said feed roller, said hydraulic motor means being drivingly attached to said web means adjacent the other end of said motor receiving means.

4. The feed rotor of claim 1 in which said feeding means comprise chain means.

5. The feed rotor of claim 1 in which said feeding means comprise serrated means.

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